Unbalance correction method and machine



Oct. 27, 1942. w so 2,300,354

UNBALANCE CORRECTION METHOD AND MACHINE Filed June 24, 1939 14 Sheets-Sheet l INVENTOR W144 14 5027-0 Eva/5m ATTORNEY Oct. 27, 1942. w. B. EDDISON 2,300,354

UNBALANCE CORRECTION IE'HIOD MID IIACHIIIB Filed June 24. 1939 14 Sheets-Sheet 2 40 29 x )Vnunn a 30 E fdfu q ATTORNEY Oct. 27, 1942. w B, s0 2,300,354

UNBALANCE CORRECTION METHOD AND MACHINE Filed June 24, 1939 14 Sheets-Sheet 3 mo E v/oo b 523. 6A. 5 6 I INVENTOR W/AAIHM Enema/1500mm kwa W ATTORNEY Oct. 27, 1942. w. a. EDDISON 3 3 UNBALANCE CORRECTION METHOD AND MACHINE Filed June 24, 1939 14 Sheets-Sheet 4 INVENTOR mu /7" MQTQNEdD/JM gldw ATTORNEY Oct. 27, 1942. w. a. EDDISON UNBALANCE CORRECTION METHOD AND MACHINE 14 Sheets-Sheet 5 Filed June 24, 1939 INV ENTOR W/wm deem fan/1M ZWM WM ATTORNEY Oct. 27, 1942.

'w. B. EDDISON UNBALANCE CORRECTION METHOD AND MACHINE l4 Sheets-Sheet 6 Filed June 24, 1939 [y QQ INVEN TOR MkL/M fimeraw 50015 on! 6 64am 1 ATTORNEY Oct. 27, 1942. w. a. EDDISON UNBALANCE CORRECTION METHOD AND MACHINE Filed June 24, 1939 14 Sheets-Sheet '7 Oct. 27, 1942. w. B. EDDISON UNBALANCE CORRECTION METHOD AND MACHINE Filed June 24, 1939 14 Sheets-Sheet 8 INVENTOR MLL/HM 8,9270 Ema/am! all 6 M ATTORNEY UNBALANGE CORRECTION METHOD AND MACHINE Filed June 24, 1939 14 Sheets-Sheet 9 INVENTOR W/uvn 60em-eomsw /u! 6 WM ATTORNEY Oct. 27, 1942.

W. B. EDDISON UNBALANCE CORRECTION METHOD AND MACHINE Filed June 24, 1939 14 Shes ts-Sheet 10 A'ITORNEY Oct. 27, 1942. w, a EDDlsON 2,300,354

UNBALANCE CORRECTION METHOD AND MACHINE Filed June 24, 1939 14 Sheets-Sheet 11 INVENTOR s b I W/M/m-v &wem- 61:01:00 5.34 0 g: 527 1715.50". rm g P Cd; 27, 1942. w 5 EDDlSON 2,300,354

UNBALANCE CORRECTION METHOD AND MACHINE Filed June 24, 1939 14 Sheets-Sheet 12 muff/17,7744

INVENTOR "Qua/4M inerm Eaa/sm ATTDRNEY Oct. 27, 1942. w. BJEDDISON 2,300,354

UNBALANCE CORRECTION METHOD AND MACHINE Filed June 24, 1939 14 Sheets-Sheet 13 INVENTOR 17/44/49: 84870 foo/son F B ATTORNEY Oct. 27, 1942. w. B.- EDDISON 2,300,354

UNBALANCE CORRECTION METHOD AND MACHINE Filed June 24, 1939 14 Sheets-Sheet 14 INVENTOR M4414 dam/v Eva/101v ATTORNEY Patented Oct. 27, 1942 UNBALANCE CORRECTION METHOD AND MACHINE William Barton Eddison, Irvington, N. 1. Application June 24-, 1939, Serial No. 280,907

22 Claims.

This invention relates to correction of unbalance in work pieces, particularly for such correction about an intended axis of rotation, and especially for relatively heavy parts such, for example, as engine fly wheels? A purpose of the invention is to provide a method or methods for balancing unbalanced work pieces, particularly adapted to be applied in whole or in part in various types of automatic or semi-automatic machines to effect improved accuracy or production, or a minimum of operators attention, or all of these improvements, during a balancing operation.

A further purpose is to provide means, such as machine units for carrying out individual steps of a balancing operation, or such as a machine for carrying out a series of such steps, and particularly for automatic or semi-automatic operation.

A further purpose is to simplify and improve the method of balancing unbalanced work pieces.

A further purpose is to simplify and improve the construction, operation and relationship of parts of machines for balancing or of individual units of such machines,

Still other objects will be apparent from this specification of the invention, it being understood that the invention includes the specific methods and structures herein illustrated, described and claimed and such other methods and structures as are equivalent to the methods or structures of the claims.

The same reference characters have been used for the same parts throughout, and in the drawings:

Figure 1 is a top view of a fly wh'eel shown in Fig. 2.

Figure 1A is a similar view of the fly wheel, rotated 90.

Figure 2 is a diagram illustrating a device for measuring unbalance in a Work piece with the intended axis of rotation vertical.

Figures 3, 3A are views respectively corresponding to Figs. 1, 1A, but showing an unbalance located in a different angular relationship.

Figure 4 is a semi-diagrammatic illustration of a device for measuring unbalance in a work piece with the intended axis of rotation horizontal.

Figures 4A, 4B show portions of the device of Fig. 4, viewed from the left.

Figure 4C is a horizontal section, enlarged, of a portion of the mechanism shown in Fig. 4.

Figure 5 is a diagram showing the operating relationship of parts of a unit for effecting a mechanical pattern of such unbalance as may be present in a work piece,

Figure 5A shows some of the parts of Fig. 5 in their relation to other parts of the same unit.

Figures 6, 6A show a pattern member used in the device of Fig. 5, respectively in plan and elevation, and enlarged.

Figure '7 is a front elevation of a machine for automatically positioning work pieces in a series of positions for successive steps of an automatic balancing operation, where the balancing is effected with the work piece in position for its intended axis of rotation to be horizontal, as in Fig. 4. Various units used in combination with the machine to carry out the improved methods of the invention have been removed to better show the mechanism of the machine.

Figure 8 is a plan view of the machine of Fig. 7.

Figure 9 is an end elevation of the machine of Figs. 7, 8, viewed from the left in Fig. 7, some of the machine structure being removed.

Figure 10 is a partial vertical section of the machine of Figs, 7, 8, taken approximately along line Ill-l0 of Fig. 8.

Figure 11 is a plan view partly broken away of a timer unit of the machine of Figs. 7, 8.

Figure 12 is an enlarged sectional view of the same unit, taken along line l2-l2 of Fig. 11.

Figure 13 is a horizontal section, showing some of the mechanism oi. the machine of Figs. 7, 8, taken approximately along line l3-l3 of Fig. 10,

Figure 14 is a. fragmentary vertical section, showing some of the mechanism of the machine of Figs. 7, 8, taken approximately along line l4l4 of Fig, 13.

Figure 14A is a vertical enlarged section taken along line MA-MA of Fig, 14, and showing some associated parts.

Figure 15 is an enlarged view of some of the mechanism of the machine of Figs. 7, 8, partly in vertical section taken approximately along line |5-l6 of Fig. 8.

Figure 16 is a partial horizontal section taken along line l6-l6 of Fig. 15.

Figure 17 is a partial vertical section of mechanism shown in Fig. 15, and associated mechanism, taken along line I'l-Il of Fig. 8.

Figure 18 is .1 semi-diagrammatic view of the arrangement and operating relationship of parts of an initial work loading unit used with the machine of Figs. '7, 8.

Figure 19 is a semi-diagrammatic partial elevation of one of the units fixed on the machine of Figs. 7, 8 and incorporating in this instance the essentials of the device of Fig. 5 for efiecting a mechanical pattern of unbalance. The unit and the machine portions are shown as they appear from the left of the machine, othrunits' being removed.

Figure 20 is a semi-diagrammatic representation showing operating relationship of parts of a unit used on the machine of Figs. '1, 8 for utilizing the mechanical pattern of unbalance effected by the unit of Figs. and 19.

Figure 21 is a vertical section of a driller unit, used with the machine of Figs. '7, 8, taken approximately along line 2 l-2l of Fig. 22, and diagrammatically showing some of the control mechanism.

F gure 22 is a front elevation of the driller unit of Fig. 21.

Figure 23 is a diagram showing the operating relationship of the control mechanism of the driller unit of Figs. 21, 22, together with its relation to the operating mechanism of a work supporting and clamping device used with the driller unit.

Figure 24 is a reduced size diagram showing an end elevation of the driller unit of Figs. 21. 22, 23 in operating position on the frame of the machine of Figs. 7, 8, as viewed from the left of Fig. 8, other units being removed.

Figure 25 is a diagram of an unbalance measuring unit, used with the machine of Figs. '7, 8 for controlling operation of the driller unit of Figs. 21, 22, etc., and. showing the operating relationship of the parts.

Figure 26 is a diagram showing the operating relationship of parts of means provided for the machine of Figs. '7, 8, for inspection of remaining unbalance after the unbalance has been corrected, and for accepting or rejecting the work pieces in accordance with the inspection result.

Figure 27 is a diagram showing the operating relationship of parts of an unloading device for the machine of Figs. 7, 8.

Figure 28 is a diagram illustrating still another method of pivoting a work piece for determination and correction of unbalance.

There will first be described some of the unbalance measuring principles used in the machines and units herein shown.

In the diagrams, Figs. 1, 2, a work piece is carried on a support 22 with the intended axis of rotation 2! vertical, the support being perfect- 1y balanced about spaced pivots such as 23. The intended rotation axis, when vertical in Fig. 2, passes through the pivot axis 23 and if the work piece is perfectly balanced the work axis is retained in vertical position, Fig. 2, by a spring 24, there being adjusting nuts 24a to adjust the spring then to have zero load. A pointer reads against a scale 26 to indicate the turning moment set up by an unbalance in either direction from the zero position.

If an unbalance exists in the work piece it may be considered for correction purposes as an undetermined weight to acting at a point which, for the present, may be assumed to be, as shown in Fig. 1, within the 090 quadrant of the work piece, at undetermined distances x and 1! respectively from the 0 and 90 radii of the axis 2i. Unbalance so located will cause a moment of rotation about pivot 23 which is equal to wa: and is weighed by the spring 24 to indicate its value on scale 26, the pointer movements being proportional to such value.

Ifthe work piece 20 is then turned clockwise ninety degrees, or such convenient angle and direction as will accomplish the purpose, on its support 22, to the position shown in Fig. 1A. the unbalance w will now set up a turning moment about pivot 23 having a value wy, which will be similarly indicated on scale 26. and a parallelowork axis horizontal,

.30, on spaced arms 3la of a lever gram of'the forces wy, waz, establishes a as the angular position of the unbalance relative to the 0 point on the work piece. From known values of was and my, determined by the deflection of pointer 25 as previously described, the value of 101' in the force parallelogram is also established. and if work piece material is removed at a point w at any radial distance 1" along the radial line now located for the unbalance w, such material removal will balance the work piece when the weight of the removed material satisfies the equation w'r'==wr. The selection of any convenient radius value for r establishes the weight of material w required to be removedfor effecting balancing; or the material can be added if preferred along the extended radial line of the unbalance at the other side of the axis 2|.

The initial position of the unbalance w in the moment measuring device of Fig. 2 may stand at any angle relative to the zero degree point on the work piece, but whatever the angle it may be determined in the manner described. Thus, for example. in Figs. 3, 3A there is shown the result when the work piece is positioned with an unbalance which, during the first measurement, is in the 180270 quadrant. whereby the correction angle is, Fig. 3A, 180+a from the zero point on the work piece.

It will be noted that during the measuring of the moments was and wy. Figs. 1, 1A, the pointer 25 moves upwardly, Fig. 2, from the zero mark on scale 26, while during the measurement of was and wy, Figs. 3, 3A, the pointer moves downwardly. The relative direction of the first and second pointer movements obtained in measurements such as described is determinative of the angle of the unbalance relative to the zero degree point on the work piece. Thus, where the upward movement of the pointer 25 is considered as positive and the downward movement as negative it will be apparent that, if both the measurements are positive the unbalance is 11 from the zero degree point on the work piece. as in Figs. 1, 1A. If the first measurement is positive and the second is negative the angle is 90+a from work piece zero. If both measurements are negative the angle is l+a from work piece zero, as in Figs. 3, 3A. If the first measurement is negative and the second is positive the angle is 270+a from work piece zero.

From the foregoing it will be apparent that. where measurement of unbalance is effected in two 99 positions of a work piece in the manner described, the amount and direction of the movements of a measuring pointer such as pointer 25, Fig. 2, together completely determine the unbalance, both as to position and amount, so far as is necessary for correction thereof.

Referring to Figs. 4, 4A, 4B, 4C the work piece 23 is supported on a frame 21 with the intended the work bearing portions resting on level pivot blocks such as 28. A member 25 provides spaced shoe or work contact portions 25a and is loosely engaged, as by screws 3i. the lever being pivoted on the frame at 32. A measuring spring 33 is rigidly fixed with frame 21 at 34 and at its outer free end carries a ball pivot portion 35 closely slidably fitted in a vertical slot of member 29. and also carries an extension rod '36. Frame 21 has fixed thereon a support 31 carrying an indicator pointer 38 pivoted at 39 and having a rearward extension 38a carrying spaced pins 40 which closely slidably engage the extension rod 36.

The lever 3| is urged by a spring 4| against a stop screw 42 and in such position the member 29 will be clear of the work piece 20. The lever may be urged in the other direction, against a stop screw 43 by the means of a solenoid 44, and in such position the member 29 contacts the work, as shown, and is free from the supporting screws 30. When in its upper position the member is urged by measuring spring 33 to a central position in which the spring is unflexed and pointer 38 stands at zero reading, and during its downward movement the member 29 contacts the work in such central position, the work meanwhile being prevented from rotating about its pivots, as later explained. Subsequently, when the work is freed, any unbalance in the work piece will set up a moment of rotation in one direction or the other about its pivot points on blocks 28 accordingly as the unbalance falls to the one or the other side of the vertical plane, Fig. 4A, of the pivots. The member 29 will tend to rotate with the work piece, whereby to de fiect spring 33 and pointer 38 in proportion to the value of the force, that is to say, the deflection will be proportional to the product of the unbalance weight and its distance from the vertical plane of the work pivot, as previously explained.

'It should be understood that angular movement of a member such as 29 with the work piece, at least theoretically, sets up some unbalance due to the member. The angular movement is ordinarily so slight that this effect is negligible but. if desired, the effect may be readily eliminated by suitable counterbalance means, not shown.

It is necessary that member 29 shall not shift relative to the work piece during the measuring operation. Various means, in addition to the contact friction set up by the weight of the member, may be used to prevent relative shifting during measuring; as, for example. suction, or increase of contact pressure, or magnetism, etc. In the present instance the member 29 is an electro-magnet, which may be energized by a coil 45.

The solenoid 44 and magnetizing coil 45, Fig. 4, may be automatically energized and de-energized at suitably timed intervals in a cycle of work operation, as follows:

A cam shaft 50, Fig. 4, may 'be timed for one rotation during a machine cycle and carries fixed thereon suitable rotary cams such as 52. Cam 5| is configurated as at 5m to suddenly release a pivoted lever 53 urged to released position by a spring 54, the release of the lever operating a pressure switch 55 to effect a contact at 55a for energizing the solenoid 44. Later in the revolution of cam 5| the lever 53 is forced back to its position opening the switch 55 and the solenoid 44 is de-energized. The rotary cam 52 similarly operates a pivoted lever 56 for closing and later opening a pressure switch 5'! in the circuit of coil 45, whereby to energize and deenergize the coil 45.

The switch operating configurations of the cams 5|, 52 are of such relative angular position and extent that the coil 45 is energized after the member 29 has been seated on the work piece 20, as previously described, and remains energized during the operation of measuring the unbalance moment of the work, and is de-energized before the member 29 is raised from the work, that is to say, before solenoid 44 is de-energized. The magnet action therefore has no effect upon the initial positioning of member 29 on the work piece, or during its release.

It will be apparent that in the device of Fig. 4, as in the device of Fig. 2, the amount and direction of indicator pointer movement obtained in two unbalance weighing operations, made respectively with the work piece 2!! in an initial position and in a second position ninety degrees rotated from the initial position, will determine the amount and angular position of any unbalance present in the work piece sufficiently for correction of the unbalance.

In Figs. 5, 5A there is shown mechanism whereby the movement of indicator devices such as pointer 25, Fig. 2, or pointer 38, Fig. 4, may be utilized for control of certain operations for correction of the unbalance.

The pointer 38, Fig. 5, is arranged adjacent to a reciprocable slide or bar 60, Figs. 5, 5A, which is guided on a support 6|. Also adjacent to the slide 60 there is an indeXi-ble carrier or support 62 upon which are equi-angularly spaced three pattern discs 63, 64, 65 each of which are rotatable on an axis parallel to the index axis of carrier 62 and also axially movable. Three index movements of carrier 52, each of 120, complete a cycle of carrier movement, and progressively moves one of the discs 63, 64, 65 through each of three disc positions A, B, C.

The slide 50 is moved in forward direction, to the left in Fig. 5, by the means of a motor 65 which is connectible to the slide by the means of a worm gear 61, a worm wheel 68 flxed on a shaft 69, a pair of meshed helical gears 70, H, a shaft 12, a pinion l3, and a rack 14 fixed with the slide. The pinion 13 is carried by a frame or housing 75 which is pivoted about the axis of shaft 69 and urged by a spring 16 against a stop 11, in which housing position the pinion is in driving engagement with rack 14. At the conclusion of the forward movement of slide 60, determined as later explained, the housing 15 is swung in the other direction against a stop 7'8 by the means of a solenoid 19, such movement disengaging the pinion l3, and the slide is then rapidly moved in reverse direction, to the right in Fig. 5, against a stop 80, 'by suitable means. such, for example, as a spring 8|. During the is connected for movement with the slide, sweeps forward to the left in Fig. 5, across whichever one of the discs 63, 64, 65 occupies the indexed position indicated as A. Also during the forward movement an electric contact member 83 carried on a bar 84, which is connected for movement with the slide 60, moves forward, to the left in Fig. 5, to effect closed contact with a contact member 8311 carried on the measuring pointer 38.

The mechanism of Figs. 5, 5A controls the reciprocation of slide 65 as follows: A cam 90 is fixed on the shaft 50, which is timed to have one revolution per machine cycle as previously stated. Cam. 90 is configurated as at 900. to release -a pivoted lever 91, at a predetermined time in the a motor switch 94, normally held open by a spring 94a. The slide 60 is then in its right-hand position against the stop and the pinion 13 is engaged with rack 14, as shown in Fig. 5, and upon the energizing of motor 66 through switch 94 the slide immediately starts movement to the left.

The closing of motor switch 94, Fig. 5, simultaneously closes a switch 95, and directly after the slide 60 starts to the left a pressure switch 98 is closed by a spring 96a, following which the solenoid 93 is energized through the switches 95, 96 independently of the switch 92. The lever 91 may then be returned to the position opening switch 92, by the means of the configuration on cam 90, the motor 66 continuing energized to move the slide 60 to the left.

During such left-hand movement the contact member 83 in the circuit of the solenoid I9, closes the solenoid circuit through the contact member 830. carried by pointer 38, whereby the housing 15, Fig. 5A, is swung to the position abutting stop 18 and disengaging pinion 13 from rack Hi and slide 60. When pinion 13 is thus disengaged the spring Bl starts movement of slide 69 to the right in Fig. 5, but this movement interrupts the circuit of solenoid 19 and in order for the slide 60 to complete its cycle to initial starting position it is necessary to provide other means to maintain the housing 15 in the position disengaging the pinion. Such means are provided as follows:

A pivoted lever or latch 960, Figs. 5, 5A, is urged by a spring 960a in a direction to disengage the latch from a rod 91 fixed on the pivoted housing 15. But when the switch 95 is closed at the time of the starting of motor 66, as previously described, a solenoid 98 is energized which urges the latch in the direction to engage a notch 91a of the rod 91. At the moment, since housing 15 is in the position abutting stop I1, such engagement is prevented by abutment of the latch against the end of the rod, but when the housing is swung to its other position, abutting stop 18, the latch will engage the notch. The switch 95 remains closed. whereby to continue to energize solenoid 95 until the motor switch 94 is opened, which occurs at the completion of the right-hand movement of slide 69, when the bar 84, just prior to the abutment of slide 69 against stop B opens the pressure switch 95, thereby interrupting the circuit through solenoid 93. When solenoid 9B is deenergized as described the spring 960a imme diately withdraws latch 960 from notch 91a and spring I then returns the housing 15 to its initial position against stop 11 and with pinion 13 engaging rack 14, but since the motor 66 is now de-energized no movement of slide 60 will take place until the cycle of slide movement is again started, as before.

From the preceding description of the operation of the cycle of movement of slide 60 it will be noted that the re-engagement of the pinion 13, just mentioned, completes the positioning of all the parts in their initial position for starting another cycle at a time determined by rotation of the cam 90. The operation of the machine herein shown requires two of the described reciprocatory movements or cycles of slide 69, respectively during the time when the pointer 38 occupies its different positions for the first and second measurement of unbalance in a specific work piece. The first cycle has just been described. The second cycle is the same except that the reversal of slide movement from left to right, Fig. 5, will probably take place at a different point in the left-hand movement, as determined by the position of pointer 38 during the second unbalance measuring operation. The

second cycle is initiated in proper timed relation similarly to the first cycle, as by a second configuration 99 of the cam 90.

Each of the discs 63, 64, 65, Fig. 5, carries a block member such as I09, these blocks being alike and square in lateral dimensions and relatively thin; an individual block being shown in Figs. 6, 6A. The blocks provide an upstanding round rod portion Iona axially vertical and centrally positioned relative to the square sides, and are cut away on their bottom face as at I091), partly to avoid rocking and also to act as magnets, the blocks being permanently magnetized. The blocks may be shifted about to any position on their discs but, being magnetized as mentioned, will be normally yieldingly retained wherever positioned.

As later explained, when a disc occupies the position C, Fig. 5, and is about to be indexed to position A, the block I00 has been returned to what may be termed its initial position relative to its disc, indicated at I-a, Fig. 5. The subsequent indexing of support 62 through to effect the disc position A carries the block along with the disc in the same relative position, but the block now has one of its side faces substantially parallel with the face 82a of the bar B2, as shown at l00l, Fig. 5. Shortly following such indexing, the first measuring operation having meanwhile been completed whereby to position pointer 38 in, for example, the full line position shown in Fig. 5, the cam 99 initiates the first cycle of reciprocatory movement of slide 69, previously described, and the relative proportion and movement of the parts is such that the forward sweep of arm face 82a positions the block I90, as at the dotted line position I09-2, Fig. 5, for its center to be spaced a distance from the disc radius line, marked 0 on the diagram, exactly proportional to the was value on the diagram Figs. 1A, 3A, that is to say, exactly proportional to the deflection of pointer 38 from its zero position, and will be at the one side or the other of the zero degree radial line accordingly as the pointer reading is in the positive direction P, or in the negative direction N.

Following positioning of the block I90 in the position Hill-2, Fig. 5, as described, the disc which is in position A is rotated 90 on its vertical axis, in the direction indicated by the arrow associated with disc 63, the disc rotation, in the present instance, positioning the block at loll-3. Shortly following such positioning. the second measuring operation with the work piece which is being measured also turned 90" for reasons previously explained having meanwhile been performed, the cam portion 99 of the cam 99 initiates the second cycle of forward movement of the slide 60. Since the first cycle of forward movement of arm face 82a positioned one side of the block exactly parallel with the face, the 90 indexing of the disc leaves the block with the side adjacent the arm face exactly parallel thereto, and the second cycle will not disturb the first setting of the block relative to the 0 radial line. In this second cycle of forward movement the pointer 38 may stand in any position of its range of movement, as determined by the unbalance in the work piece, as, for example, in a negative reading position indicated by the dotted lines, Fig. 5, but, whatever the pointer position, the forward movement of the arm face 82a will position the block Hill, as for example at the position i903, Fig. 5, with its center at a distance from the 90 radius of the disc which is exactly pro portioned to the wy value of the diagrams, Figs. in, BA, measured in the second measuring operarun.

It will be apparent that in the position I-4 of the block I00, established as described, the position of the center or axis of the round portion I00a of the block relative to the axis and 0 radial line of the disc which is in the position A establishes what may be termed a mechanical pattern of a force diagram such as the diagram Figs. 1A, 3A, in which the center of the block stands on a radial line corresponding to the angular position of any unbalance in the work piece used to establish the position of the block, and such pattern may be utilized to effect correction of the unbalance, as later explained. Also, the radial distance of the center of the block from the disc axis represents the value wr of the force diagram whereby the radial position of the block may be used, if desired, to control the amount of material removed, or added, to correct the unbalance.

The measuring and recording methods described may be incorporated in a variety of ways in machines for the balancing of work pieces. In Fig. 7 there is shown a machine for automatically balancing fly wheels, utilizing a cycle of operations which measures the unbalance of the individual fly wheel while the intended axis of fiy wheel rotation is horizontal, as in the method explained for the device of Fig. 4. The machine also utilizes, as a part of its cycle of operations, the method of transferring the unbalance measurements to a mechanical pattern, as explained in connection with the diagram, Fig. 5, together with various other coordinated cycles and methods, as will be explained.

Referring particularly to Figs. 8, 7, 9, the balancing machine is intended to operate on fly wheels which have been delivered, as by a suitable conveyor, to an initial position adjacent the machine, indicated at Il2a, Fig. 8, the fly wheels being picked up by the machine to proceed through a step-by-step sequence of positions and of operations including unbalance measuring, correcting and inspection, and at the completion of the several operations the fiy wheel, provided it is found upon inspection to be balanced with predetermined limits, is delivered to a position indicated at H27, from which it may be removed by any suitable conveyor.

The machine operates simultaneously upon several fly wheels respectively in different positions, as will be explained, and the time required to complete a fly wheel is therefore only a fraction of the time required for the fly wheel to pass through the machine, being no greater than the time required for one operation of the sequence.

The machine includes a stationary frame II3, Fig. 8, with which are fixed horizontally spaced parallel rails or supports I I4, I I la between which the fly wheels are moved during their progress through the machine. A primary drive shaft H is driven continuously from any suitable power source, not shown, and continuously reciprocates a slide-rod I I 6, the rod being guided in the frame for right and left-hand movements, Fig. 7, and reciprocated through a worm III, a worm wheel H8, a crank H9 fixed with the worm wheel and a. connecting rod I pivoted at the one end on the crank and at the other end on a. cross-arm member I2| which is rigidly fixed with the sliderod. At its one end the cross-arm has rigidly fixed therewith an arm or bracket I22 carrying a selector-timer unit generally denoted by the rier I49 has similar movement.

numeral I23, Figs. 7, 11. The unit I23 is therefore continuously reciprocable from the drive shaft H5.

The reciprocatory unit I23 is provided with a plurality of sets of actuator dogs and control cams therefor, the sets being respectively generally denoted as I24, I25, I26, I21, I28, Fig. 11. The set I27, shown in Fig. 12, is illustrative of each of the sets. For each set there is provided a pair of cams such as I23, I30 respectively fixed on cam shafts I3I, I32 which are rotatably mounted in the frame of the unit I23 and geared together for opposite directions of rotation by the meshed gears I33, I34, Fig. 11, the cam shaft I3I having fixed therewith a ratchet wheel I35. As best shown in Fig. 7, a ratchet dog I36, which is pivoted on frame H3, is adapted to engage ratchet wheel I35 at each reciprocatory movement of unit I23 to the right in Fig; 7 and operates to turn the ratchet wheel, together with the cams such as I29, I30, through an angular movement corresponding to the angular spacing of the teeth on the wheel. Each cam pair of the different sets is provided with suitable configurations such as I29a, I30a, Fig. 12, cooperating to effect pivotal movement of a pair of cam dogs such as I38, I 39 whereby to position either dog with its inner end raised upwardly by suitable means, such as springs, not shown, to effect a pushing engagement with an abutment block, such as I40, carried by a slide such as I41 which is reciprocably guided on the machine frame. When the cams of a pair of dogs are in a position where neither dog is raised as described, the corresponding slide remains stationary in the position where last shifted, until the reciprocatory movements of the unit I23 have turned the cams to raise one of the dogs to abutting position.

It will be apparent that, by the means of the different sets of actuator dogs and cams of the unit I23 slides, such as the slide II, respectively associated with the difierent sets, may be moved in either direction during a reciprocatory movement of the unit I23, or may remain stationary at either end of the reciprocatory slide movement while the unit I23 effects one or more cycles of reciprocation, accordingly as the cams are configurated.

The dog-cam set I24, Fig. 11, of the unit I23 operates a reciprocably guided slide I42, Figs. 9, 13 in the manner previously described, the abutment block for this slide being offset from the slide as shown in Fig. 10. The dog-cam sets I25, I26, I21, I28 respectively similarly operate slides I43, I45, I46, M1, the slide I43 being relatively short, as best shown in Fig. 13, and guidedon a bar I44 which is fixed with the machine frame.

The slide hi2, Figs. 10, 13, is connected for timed movements both of a loading carrier I48, Figs. 7, l8, and of an unloading carrier I49, Figs. 7, 27. The loading carrier I48 moves between the positions respectively shown in full and dotted lines, Fig. 18, whereby to first receive the work piece as it is shifted from the position II2a. to the position H21), and next to move the work piece to the position 20. The unloading car- It receives the work piece in the position 211., Figs. 7, 27, and delivers the piece to position II2i. The slide I 42 is connected to effect the movements mentioned through a connector arm I50, Fig. 13, rigidly fixed with the slide and with a correspondingly reciprocable bar I5I having angular rack teeth I5I a meshed with a gear segment I52, Figs. 9, 13,

fixed on a shaft I53, the shaft having a lever I54 fixed thereon and connecting with the loading carrier I46 through a pivoted rod I55 and a lever I56, Fig. 8, fixed on a shaft I51 upon which is also fixed the loading carrier I48; the shaft I53 also having another lever I56 fixed thereon and connecting with the unloading carrier I45 through a pivoted connector rod I59 and a lever I66, Fig. 8, fixed on a shaft I6I upon which is also fixed the unloading carrier I49.

The operations on the machine of Figs. '1, 8, require that the fly wheel be rotated on its own axis in each of the positions II2d, II2e, 25/. For such rotation there are provided similar rotator units each including a pair of spaced wheels for supporting and rotating the work piece. For the position Il2d there is a pair of such wheels I62, I63, Fig. 8. For the position II2e there is a pair of Wheels I64, I65. For the position II2g there is a pair of wheels I66, I61. In Fig. 8 the wheels are shown in the positions they occupy during the supporting and rotation of the fly wheels. The supporting wheels must be withdrawn axially, downwardly in Fig. 8, from such positions in order to transfer the fly wheels from one station to another, as later described. The supporting wheels are, therefore, mounted for such axial and rotary movement in a manner which is similar for each pair of supporting wheels except as later pointed out. The mounting and arrangement of drive gears for the supporting wheel pair I62, I63 includes parallel shafts such as I66, I69, Fig. 8, on which the wheels are fixed, the shafts each being journaled at axially spaced points in bearing members such as I16, I1I for the wheel pair I62, I63, and in bearing members I12, I13 for the wheel pair I64, I65, and in bearing members I14, I15 for the wheel pair I66, I61. The bearing members I14, I15 are supported for vertical movement, Fig. 9, on a vertical slide bar I16, Figs. 8, 9, and the bearing members I16, I1I are supported for similar vertical movement on a vertical slide bar I11, Fig. 8, these slide bars being simultaneously shifted vertically at intervals, as later explained. The wheel pair I64, I65 requires no vertical movement and the bearing members I12, I13 for this wheel pair are suitably rigidly fixed on the machine frame. The bearings of the roll shafts in the bearing members act as guides for the axial shaft and roll movement and for each roll pair there are gears such as I18, I16, Fig. 8, fixed on the respective shafts, each gear engaging with an axially stationary drive pinion such as I86, Fig. 7, also journaled in the bearing members. The corresponding drive pinions for the other roll pair units are indicated at IBI, I82, Fig. '1.

The supporting roll pairs I62, I63, etc., are all simultaneously shifted to the left, Fig. 9, to their fiy wheel supporting and rotating positions there shown and shown in Fig. 8; or alternatively oppositely simultaneously shifted to a position permitting transfer of the fly wheels from one station to another, by the reciprocatory movements previously explained of the slide I45, Fig. 13. At its right-hand end, Fig. 13, the slide I45 is provided with angular rack teeth I83 which continuously engage with correspondingly angular teeth on agear segment I64 which is fixed on a shaft I65 that is iournaled in the machine frame and extended axially for the support of two similar levers I66, I61, Figs. '1, 6, 9, the end of each lever being slotted to engage shifter pins such as I68, I89, the pins being fixed at the opposite ends of a laterally and vertically movable support bar I96, Fig. '1. The support bar I96 is fixed rigidly with spaced arms I9I, I92 which are coaxially pivoted on the machine frame; the pivot of the arm I9I being shown at I9Ia, Fig. 9, and of the arm I92 at IBM, Fig. '1. At suitable spacing along the bar I96 there are provided upstanding arms or members, rigidly fixed with the bar, for the axial shifting of each of the roll pairs I62, I63; I64, I65 and I66, I61. The shifter arm members for the roll pair I62, I63 are illustrative. Referring to Figs. '1, 8, shifter arm members such as I95, I96 are provided with spaced outstanding fork portions such as the fork portions I95a, I96a, the respective fork portions engaging opposite end faces of the gears I16, I19 to effect the shifting.

By the described mechanism, as the reciprocatory slide I45 is moved to the left in Fig. 13 the supporting roll pairs I62, I63; I64, I65; and I66, I61, Fig. 8, are simultaneously withdrawn from their fly wheel supporting positions, downwardly in Fig. 8 from the position there shown; and as the slide I45 is moved to the right in Fig. 13 the roll pairs are returned to their Fig. 8 positions, each of these movements taking place at timed intervals determined by the selectortimer unit I23, in the manner previously explained.

For each of the fly wheel positions Il2d, H2 Il2g, the balancing operation requires supporting a fly wheel on pivot blocks with its axis horizontal, and for these positions there are provided pivot block pairs such as 266, 26I; 262, 263; and 264, 265, Figs. '1, 8, the different blocks of a pair being respectively fixed on the rails I I4, 40.. For the fly Wheel position II2d and H29 the operations require that the fly Wheels be lifted off the pivot blocks and rotated as later explained. It is to effect such lifting for these positions that the fly wheel supporting roll pairs I62, I63 and I66, I61, Fig. 8, are vertically movable with the slide bars I16, I11, as previously mentioned.

The reciprocatory movement of the slide I42,

, Fig. 13, in addition to effecting the movement of the loading carrier I46 and unloading carrier I49 as previously explained, also effects the vertical movement of the supporting roll pairs I62, I63 and I66, I61 just referred to. The slide bars I16, I11, Fig. 8, in their downward extension, each operate in spaced guide members fixed on the frame, such as members 266, 261 and 266, 269, Figs. '1, 13, and the bars respectively carry shifter pins 2I6, 2I I, Fig. 13, each engaging angular cam slots in the slide I42, the cam slot for the vertical slide bar I16 being best shown at 2I2 in Fig. 14, the slot for the other bar I11 being similar. It will be seen that as the reciprocable slide I42 is moved to the left from the position shown in Fig. 14 the slide bars I16, I11 and the roll pairs I66, I61 and I62, I63 respectively carried thereby will be moved upwardly, and during the right-hand movement of slide I42 these roll pairs will be moved downwardly, such upward and downward movements being suitably timed by the selector-timer unit I23.

The rotation of the supporting roll pairs I62, I63 and I66, I61, Fig. 8, for effecting 90 turning of the fiy wheel when in positions HM and H29, takes place after the roll pairs have been shifted upwardly, as just I described, whereby the fly wheel is lifted from its pivot blocks during such rotation. Such 96 fiy wheel rotation is effected by the reciprocatory movement of slide I43. Referring to Fig. '1, the slide I43 carries an arm 2I5 

